WO1999030059A1 - Engrenage a friction variable en continu - Google Patents

Engrenage a friction variable en continu Download PDF

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Publication number
WO1999030059A1
WO1999030059A1 PCT/EP1998/007894 EP9807894W WO9930059A1 WO 1999030059 A1 WO1999030059 A1 WO 1999030059A1 EP 9807894 W EP9807894 W EP 9807894W WO 9930059 A1 WO9930059 A1 WO 9930059A1
Authority
WO
WIPO (PCT)
Prior art keywords
input
output
disks
gear
shaft
Prior art date
Application number
PCT/EP1998/007894
Other languages
German (de)
English (en)
Inventor
Bernhard Sich
Original Assignee
Zf Friedrichshafen Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Priority to US09/555,070 priority Critical patent/US6402657B1/en
Priority to EP98965762A priority patent/EP1038124B1/fr
Priority to DE59802003T priority patent/DE59802003D1/de
Publication of WO1999030059A1 publication Critical patent/WO1999030059A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
    • F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
    • F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces

Definitions

  • the present invention relates to a continuously variable friction gear according to the preamble of claim 1.
  • Such a continuously variable friction wheel transmission usually has input and output disks arranged coaxially to a common shaft, which are arranged in pairs to one another and whose inner surfaces are designed in a toroidal shape, and friction wheels arranged between the pairs of input and output disks.
  • These friction wheels are in frictional contact with both the input disks and the output disks and transmit the torque transmitted to them from the input disk to the output disk by frictional contact, the speed of the friction wheels being greater the greater the distance between their contact point with the input disk and is the axis of rotation.
  • the speed of the output disks is greater the closer the point of contact between the friction wheel and the output disk is to the axis of rotation.
  • the speed of the output disk can therefore be adjusted continuously and arbitrarily.
  • the axes of rotation of the friction wheels are mounted on a carrier which can be controlled via a pivoting device.
  • the transmission according to US Pat. No. 3,739,658 also has a two-pass variator with two input and output disks arranged in pairs, between which pivotally mounted friction wheels are arranged.
  • a bearing support which is part of the housing and which is arranged spatially between the two output disks.
  • the power flowing away from the output disks is fed to a hollow shaft via a planetary gear, which also acts as a differential.
  • the hollow shaft is non-rotatably connected to the output gear and is rotatably held via ball bearings in the bearing support.
  • the output gearwheel is connected to a gearwheel connection which is attached to the housing of a torque converter in a rotationally fixed manner. This drives the transmission output shaft.
  • the arrangement of the torque converter at the input of the output shaft requires a relatively large center distance between the input and output shaft of the gearbox. The application cases for this gearbox are therefore severely restricted because the required installation space is not always available.
  • a continuously variable friction gear is known with an input shaft that passes through a housing.
  • the housing is divided into two cavities by means of a partition m, each of which has an input disk and an opposing output disk with friction wheels in between, both the input disk and the output disk m lying in the two cavities on a common axis to which the friction wheels are connected Achieving the desired speed translation can be pivoted.
  • the two pairs of input disks and output disks are arranged mirror-symmetrically to one another in the cavities in such a way that the two output disks lie next to one another, on both sides of the partition wall separating the two cavities, which has a gearwheel mounted between the two output disks the output torque is applied.
  • the object of the present invention is to reduce the construction costs of such a continuously variable transmission and to reduce the manufacturing costs.
  • the invention achieves the object in a generic continuously variable friction gear, which in addition to the features of the preamble also has the feature of the characterizing part of the main claim.
  • An advantageous structural design is described in the subclaim. The advantages which can be achieved with the invention consist in the use of considerably less fixed or moving parts.
  • Fig. 2 is a radial section along the line II / II of Fig. 1 and
  • Fig. 3 shows a radial section along the same
  • the friction gear 1 (or toroidal gear) has an input shaft 3, which with a starting element, not shown, for. B. is connected to a torque converter or a wet starting clutch of a prime mover of a motor vehicle.
  • the gearbox contains two gearbox units which are arranged coaxially with the input shaft 3.
  • One gear unit has an input disk 5 and an output disk 6, the mutually facing surfaces of which are designed in a toroidal shape; the other gear unit has an input disc 12 and an output disc 11, the mutually facing surfaces are also toroidal.
  • two friction wheels are preferably provided, which are attached to pivotable carriers; the friction wheels are in frictional contact with the two surfaces of the input disks 5, 12 and the output disks 6, 11 facing them, the friction wheels of each gear unit being arranged symmetrically to the axis of the input shaft 3.
  • the disks 5, 6, 11, 12 are mounted on a torque shaft 20 which can be displaced slightly in the axial direction relative to the input shaft.
  • the input disk 5 of the one gear unit is connected to the torque shaft 20 in a rotationally fixed manner, but is axially slidably mounted thereon via a spherical locking arrangement 19 (ball splme).
  • the input disk 12 of the other gear unit is also connected to the torque shaft 20 in a rotationally fixed manner by means of driving teeth.
  • the two output disks 6, 11 of the two gear units are arranged mirror-symmetrically to one another and next to one another in the gear and are arranged on a common bushing, the output disk 11 being fixedly connected to a toothed wheel 8 which rotatably surrounds the torque shaft 20.
  • Input shaft 3 is mounted and is connected to it in a rotationally fixed manner, wherein it acts on the input disk 12 m in the axial direction to the output disk 11 hm with the aid of the pressing device 4.
  • the disk 10 is mounted on the input shaft via a regulating device 17.
  • the universal bearing 18, which replaces the conventional axial bearing and the conventional radial bearing of the input disk 5, absorbs all radial and axial forces which act on the input disk 5. It is preferably designed as a ball bearing that engages on the one hand in a semi-circular recess 21 machined in the input disk and on the other hand m in a complementarily designed recess 22 in the axial flange 9. These two recesses are advantageously arranged at a high offset from one another. 7 with a cup-shaped bearing support member is designated, m the gear 8 is mounted and which separates the two gear units from each other. With 13, 14, the upper transverse oche are designated and with 15 and 16 pins for the wearer of the friction wheels, which are fastened in the holding frame 2 by means of a suitable fastening device.
  • Fastening pin 16 for receiving the upper cross yoke 13 is provided with a curved outer surface, at which the opening of the transverse oches 13 touches it.
  • the friction wheels 27, 27 ' are inserted into the recesses 28, 28' with the supports 26, 26 'and are mounted eccentrically therein, the eccentric section 29, 29' passing through the support 26, 26 'and the eccentric section 30, 30' the friction wheels 27 , 27 'carries.
  • FIG. 3 now shows the radial section through a considerably simplified support mounting in the continuously variable friction wheel gear designed according to the invention.
  • two cutouts 35, 35 ' are provided, which engage the upper ends 36, 36' of the carriers 26, 26 '.
  • a bearing 37, 37 ' is provided, which can be designed as a plain bearing or a ball bearing. This bearing 37 allows the free rotation of the carrier 26 m of the recess 35 and that caused by the hydraulic piston 32
  • a holder 39 On the underside of the housing 38 there is a holder 39 connected to it, which recesses 40, 40 'are also incorporated, m which engage the lower ends 42, 42' of the supports 26, 26 ', which are connected to the holders 34, 34 'are connected.
  • the invention thus offers a considerable simplification of the construction of a continuously variable friction wheel transmission, since both the upper and lower journals with the associated ones Fastening devices and the upper and lower transverse yokes can be omitted.
  • the support is much stiffer; The manufacturing costs are also reduced because fewer parts and, above all, fewer moving parts are required.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

L'invention concerne un engrenage à friction variable en continu qui comporte un arbre d'entrée (3) et un arbre de transmission de couple (20), disposé coaxialement par rapport audit arbre d'entrée (3), ainsi que deux disques d'entrée (5, 12) et deux disques de sortie (6, 11) disposés par paires, entre lesquels sont placées des roues de friction qui sont fixées sur des supports (26). Dans la section supérieure (39) du carter de l'engrenage sont ménagées des cavités (35) dans lesquelles s'engagent, avec un certain jeu, les extrémités supérieures (36) des supports (26).
PCT/EP1998/007894 1997-12-10 1998-12-04 Engrenage a friction variable en continu WO1999030059A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US09/555,070 US6402657B1 (en) 1997-12-10 1998-12-04 Infinitely variable friction gear
EP98965762A EP1038124B1 (fr) 1997-12-10 1998-12-04 Engrenage a friction variable en continu
DE59802003T DE59802003D1 (de) 1997-12-10 1998-12-04 Stufenloses reibradgetriebe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19754725.7 1997-12-10
DE19754725A DE19754725A1 (de) 1997-12-10 1997-12-10 Stufenloses Reibradgetriebe

Publications (1)

Publication Number Publication Date
WO1999030059A1 true WO1999030059A1 (fr) 1999-06-17

Family

ID=7851322

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1998/007894 WO1999030059A1 (fr) 1997-12-10 1998-12-04 Engrenage a friction variable en continu

Country Status (4)

Country Link
US (1) US6402657B1 (fr)
EP (1) EP1038124B1 (fr)
DE (2) DE19754725A1 (fr)
WO (1) WO1999030059A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10339361A (ja) * 1997-06-09 1998-12-22 Nippon Seiko Kk トロイダル型無段変速機
WO2000034687A1 (fr) * 1998-12-07 2000-06-15 Zf Friedrichshafen Ag Engrenage a friction a reglage continu

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19820071A1 (de) * 1998-05-06 1999-11-11 Zahnradfabrik Friedrichshafen Stufenloses Reibradgetriebe
DE19947851C2 (de) * 1999-04-07 2003-10-16 Nsk Ltd Stufenlos verstellbares Toroidgetriebe
US6592491B1 (en) 1999-04-07 2003-07-15 Nsk Ltd. Toroidal type continuously variable transmission
DE19948756A1 (de) * 1999-10-09 2001-04-12 Zahnradfabrik Friedrichshafen Stufenloses Reibradgetriebe
DE10034373A1 (de) 2000-07-14 2002-01-24 Zahnradfabrik Friedrichshafen Stufenloses Reibradgetriebe
DE10034453A1 (de) 2000-07-15 2002-01-24 Zahnradfabrik Friedrichshafen Stufenloses Reibradgetriebe
DE10034454A1 (de) 2000-07-15 2002-01-24 Zahnradfabrik Friedrichshafen Stufenloses Reibradgetriebe
US6935988B2 (en) 2000-08-04 2005-08-30 Zf Friedrichshafen Ag Infinitely variable toroidal drive
DE10038225A1 (de) * 2000-08-04 2002-02-14 Zahnradfabrik Friedrichshafen Stufenloses Reibradgetriebe
DE10121487A1 (de) * 2001-05-03 2002-11-07 Zahnradfabrik Friedrichshafen Stufenloses Reibradgetriebe
DE10121489A1 (de) * 2001-05-03 2002-11-07 Zahnradfabrik Friedrichshafen Stufenloses Reibradgetriebe
JP2003028255A (ja) * 2001-07-19 2003-01-29 Nsk Ltd トロイダル型無段変速機
DE10206200A1 (de) * 2002-02-15 2003-08-28 Daimler Chrysler Ag Toroidvariator
US20070049449A1 (en) * 2005-03-18 2007-03-01 James Klassen Power transfer device
US7472677B2 (en) 2005-08-18 2009-01-06 Concept Solutions, Inc. Energy transfer machine
GB2455337A (en) * 2007-12-06 2009-06-10 Infinitrak Llc Toroidal variator with damped control lever
GB0920546D0 (en) * 2009-11-24 2010-01-06 Torotrak Dev Ltd Drive mechanism for infinitely variable transmission

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1833475A (en) * 1930-10-29 1931-11-24 Hartford Special Machinery Co Variable speed transmission
US3164025A (en) * 1963-03-20 1965-01-05 Curtiss Wright Corp Toroidal drive hydraulic stop
US3299744A (en) * 1963-09-04 1967-01-24 Excelermatic Toroidal-type transmission
US4526051A (en) * 1983-03-18 1985-07-02 Excelermatic Inc. Infinitely variable traction roller transmission speed control arrangement
EP0172023A1 (fr) * 1984-08-15 1986-02-19 Excelermatic Inc. Engrenage à friction et à commande hydraulique continue
US4614125A (en) * 1983-09-12 1986-09-30 Nippon Seiko Kabushiki Kaisha Infinitely variable traction roller transmission
US4955246A (en) * 1988-05-27 1990-09-11 Nissan Motor Co., Ltd. Continuously variable traction roller transmission
EP0459291A1 (fr) * 1990-05-22 1991-12-04 Nissan Motor Co., Ltd. Variateur continu de vitesse à rouleaux de traction

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2152796A (en) 1935-03-13 1939-04-04 Erban Patents Corp Variable speed transmission
US3739658A (en) 1971-06-07 1973-06-19 Gen Motors Corp Transmission
JP2638896B2 (ja) 1988-03-07 1997-08-06 日産自動車株式会社 トロイダル無段変速機
JP2715444B2 (ja) * 1988-05-17 1998-02-18 日産自動車株式会社 トロイダル式無段変速機
JP2663672B2 (ja) * 1990-04-04 1997-10-15 日産自動車株式会社 摩擦車式無段変速機の油圧制御装置
JPH10274300A (ja) * 1997-03-31 1998-10-13 Isuzu Motors Ltd トロイダル型無段変速機

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1833475A (en) * 1930-10-29 1931-11-24 Hartford Special Machinery Co Variable speed transmission
US3164025A (en) * 1963-03-20 1965-01-05 Curtiss Wright Corp Toroidal drive hydraulic stop
US3299744A (en) * 1963-09-04 1967-01-24 Excelermatic Toroidal-type transmission
US4526051A (en) * 1983-03-18 1985-07-02 Excelermatic Inc. Infinitely variable traction roller transmission speed control arrangement
US4614125A (en) * 1983-09-12 1986-09-30 Nippon Seiko Kabushiki Kaisha Infinitely variable traction roller transmission
EP0172023A1 (fr) * 1984-08-15 1986-02-19 Excelermatic Inc. Engrenage à friction et à commande hydraulique continue
US4955246A (en) * 1988-05-27 1990-09-11 Nissan Motor Co., Ltd. Continuously variable traction roller transmission
EP0459291A1 (fr) * 1990-05-22 1991-12-04 Nissan Motor Co., Ltd. Variateur continu de vitesse à rouleaux de traction

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10339361A (ja) * 1997-06-09 1998-12-22 Nippon Seiko Kk トロイダル型無段変速機
WO2000034687A1 (fr) * 1998-12-07 2000-06-15 Zf Friedrichshafen Ag Engrenage a friction a reglage continu

Also Published As

Publication number Publication date
EP1038124A1 (fr) 2000-09-27
DE19754725A1 (de) 1999-06-17
EP1038124B1 (fr) 2001-10-31
DE59802003D1 (de) 2001-12-06
US6402657B1 (en) 2002-06-11

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